US3831490A - Fluid pressure operable servo positioner - Google Patents

Fluid pressure operable servo positioner Download PDF

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Publication number
US3831490A
US3831490A US00289754A US28975472A US3831490A US 3831490 A US3831490 A US 3831490A US 00289754 A US00289754 A US 00289754A US 28975472 A US28975472 A US 28975472A US 3831490 A US3831490 A US 3831490A
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Prior art keywords
spring
spring retainer
operating rod
axial movement
piston
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Expired - Lifetime
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US00289754A
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English (en)
Inventor
P Olson
H Knight
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Bosch Rexroth Corp
Westinghouse Air Brake Co
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Westinghouse Air Brake Co
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Priority to US00289754A priority Critical patent/US3831490A/en
Priority to JP48097384A priority patent/JPS4992494A/ja
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Publication of US3831490A publication Critical patent/US3831490A/en
Priority to JP1977004787U priority patent/JPS5325120Y2/ja
Assigned to BANKERS TRUST COMPANY reassignment BANKERS TRUST COMPANY SECURITY INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: AMERICAN STANDARD INC., A DE. CORP.,
Assigned to BANKERS TRUST COMPANY reassignment BANKERS TRUST COMPANY SECURITY INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: FLUID POWER INC.
Assigned to FLUID POWER INC., A CORP. OF DE reassignment FLUID POWER INC., A CORP. OF DE RELEASED BY SECURED PARTY (SEE DOCUMENT FOR DETAILS). Assignors: BANKERS TRUST COMPANY
Assigned to AMERICAN STANDARD INC. reassignment AMERICAN STANDARD INC. RELEASED BY SECURED PARTY (SEE DOCUMENT FOR DETAILS). Assignors: BANKERS TRUST COMPANY
Assigned to REXROTH CORPORATION, THE reassignment REXROTH CORPORATION, THE ASSIGNMENT OF ASSIGNORS INTEREST. Assignors: AMERICAN STANDARD INC., A CORP OF DE
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B13/00—Details of servomotor systems ; Valves for servomotor systems
    • F15B13/16—Special measures for feedback, e.g. by a follow-up device
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B9/00—Servomotors with follow-up action, e.g. obtained by feed-back control, i.e. in which the position of the actuated member conforms with that of the controlling member
    • F15B9/02—Servomotors with follow-up action, e.g. obtained by feed-back control, i.e. in which the position of the actuated member conforms with that of the controlling member with servomotors of the reciprocatable or oscillatable type
    • F15B9/08—Servomotors with follow-up action, e.g. obtained by feed-back control, i.e. in which the position of the actuated member conforms with that of the controlling member with servomotors of the reciprocatable or oscillatable type controlled by valves affecting the fluid feed or the fluid outlet of the servomotor

Definitions

  • ABSTRACT A servo positioner for selectively positioning a machine component or device in accordance with a preselected fluid pressure signal input.
  • An operator controlled actuator when subjected to a preselected control pressure signal, causes a valve portion to transmit operating fluid pressure to a power cylinder for positioning the machine part or device connected thereto at a position determined by the degree of the control pressure signal, and a force-balancing portion for counter-balancing the force exerted by the power cylinder for maintaining the preselected position thereof and for restoring the valve portion to a neutral position.
  • Servo positioners are used extensively in numerous applications.
  • a servo positioner may be used in controlling variable pitch propellers, engine governors, steering. mechanism, or steam valves.
  • servo positioners may be used for positioning potentiometers, butterfly valves, squeeze rolls, hopper gates, torque converters, or hydrostatic transmissions. With so many applications, as those just mentioned, it is important that the servo positioner be. positive in its action, quick to respond to a control impulse, and therefore freeof hysteresis.
  • the object of the present invention is to provide a servo positioner characterized by reliability of operation by possessing the ability to respond to a control impulse without hesitation and to positively move the device or machine part to the precise position desired and to maintain said device or machine part in the desired position without variation unless a change in position is effected by the operator.
  • the servo positioner embodying the invention comprises a friction free piston actuator responsive to a control pressure impulse at a degree selected by the operator for effecting operation of an operationally sensitive valve device to cause operating fluid pressure to be supplied to a power cylinder device connected to the machine part or device to be positioned.
  • a caged spring device operatively interposed between the valve actuator and the power cylinder device is subjected to and therefore placed under tension by a force acting in one direction, as provided by the control pressure acting on the actuator, and to an opposing force provided by operating pressure supplied to the power cylinder device, until said opposing force balances said one force sufficiently to effect restoration of the valve device to a neutral or cut-off position in which further supply of operating pressure to the power cylinder is cut off and the position thereof established, unless the operator effects a change in the degree of the control impulse.
  • the power cylinder device may be set up so that the zero or neutral position of the piston is at the midpoint of the travel stroke and movable in either direction therefrom, or so that the zero or neutral position of the piston is at one extreme end of the travel stroke and movable away from and back toward the neutral position.
  • a double diaphragm actuator may be used for either set up of the power cylinders by providing a pair of control pressure inlet ports for altematively pressurizing one of the diaphragms for obtaining the desired direction of movement of the power piston in which the zero position isat midpoint, or by using just one of the ports for pressurizing and depressurizing the appropriate one of the diaphragms for obtaining movement of the piston having the zero or neutral position at one end.
  • FIG. I is an elevational schematic view, in section and in outline, of a servo positioner apparatus embodying the invention
  • FIG. 2 is an elevational schematic view, partly in section, of a modified version of the servo positioner shown in FIG. 1.
  • the servo positioner apparatus generally comprises a control valve device 1, a caged spring or force balancing device 2, and a power cylinder device 3.
  • the valve device 1 may be of any suitable type which will provide the desired operational results, but preferably is a spool type such as disclosed in a copending application assigned to the assignee of the present application and disclosed in Case No. 6596 of the Westinghouse Air Brake Company, Wilmerding, Pa.
  • Valve device l is shown in simplified form and, as shown, comprises a casing 4 in which an actuator portion 5 and a valve portion 6 are coaxially operably disposed.
  • the actuator portion 5 is provided with a double-acting actuator piston 7 alternatively subjectable, at the operators discretion, to control fluid at a selected pressure on opposite sides thereof via respective control pressure inlet ports 8 and 9, whereby the desired direction of travel of the piston may be effected.
  • the valve portion 6 comprises a spool valve member 10 connected to piston 7'by a valve stem 11, said spool valve, valve stem and piston all being arranged in axial alignment for uniform axial movement together.
  • Spool valvel0 is provided with guide'lands l2 andl3 at each end, respectively, and with two valve lands 14 and 15 axially spaced on said valve member so as to control communications between a fluid'pressure supply port 16, delivery ports 17 and'l8', andexhaust ports 19 and 20.
  • land 14 is effective for cutting off communication of delivery port 17 with both supply'port l6 and exhaust port 19
  • land 15 is effective for cutting off communication of delivery-port l8with both supply port 16 and exhaust port 20.
  • pressurization of the left side of piston 7, as viewed in the drawing, causes rightward movement of spool valve 10 to a first supply-exhaust position in which land 14 moves to the right of delivery port 17 to continue to isolate supply port 16 from said delivery port which is placed in communication with exhaust port 19, and land 15 moves to the right of delivery port 18 to continue to isolate exhaust port 20 from said delivery port 18 which is placed in communication with supply port 16.
  • depressurization of the left side of piston 7 andpressurization of the right side thereof, asviewed in the drawing produces leftward movement of spool valve 10 and a reversal of the communications between the several ports consistent with that above described.
  • valve device I is preferably of the type providing maximum friction-free movement of both the piston 7 and spool valve 10, as well as instant flow of fluid pressure between the several ports in accordance with'the position of said spool valve.
  • the particular details of the'construction of the valvedevice l are not essential to an understanding of the invention disclosed herein, but are fully disclosed and explained in the aforementioned copending application. For this reason the valve device 1 is shown in the drawings in simplified form and in a disproportionately smaller scale relative to the caged spring device 2 and the power cylinder 3.
  • Delivery port 17 is connected via a pipe or conduit 21 to the left side of power cylinder device 3, as viewed in the drawing, whereby the corresponding side of a power piston 22 operably disposed therein may be subjected to fluid pressure for causing rightward movement of said piston from a zero or neutral position in which the piston occupies a position midway between the two ends of the cylinder, as shown in the drawing.
  • Delivery port 18 is connected via a pipe or conduit 23 to the right side of power cylinder device 3 for causing leftward movement of piston 22 when the right side of said piston is pressurized.
  • a bracket 24 to which both the control valve device 1 and the power cylinder device 3 are secured, serves also for retaining the two devices in proper disposition relative to each other.
  • the outer end of rod 25 is provided with a screw-threaded stud portion 26 by which said power cylinder may be connected to a machine part or device, for example (neither of which is shown) to be operated thereby.
  • connecting bar 27 One end of a connecting bar 27 is secured to and movable with the outer end of piston rod 25 in perpendicular relation thereto, the other end of said connecting bar having one end of a guide rod 28 secured in perpendicular relation thereto and parallel to.piston rod 25.
  • Guide rod 28 extends away from connecting bar 27 and slidably through a guide bore (not shown) of a support arm 29 rigidly secured to and depending from the underside of casing 4 of control valve device 1.
  • a generally cylindrical spring cage 30 of the force balancing device 2 provides connecting means to the connecting bar 27 by being perpendicularly secured thereto between the ends of the connecting bar so that said spring device is generally disposed between and axially parallel to control valve device 1 and power cylinder device 3. It should be obvious that movement of connecting bar 27 with piston 22 causes corresponding axial movement of spring cage 30.
  • the opposite end of the spring device 2 is operatively connected through a linkage system to the piston 7 of the control valve device 1, said linkage system comprising a fulcrum member 31 disposed in axially parallel relation to piston 7 by having one end secured to the left end of casing 4 of valve device 1.
  • fulcrum member 31 forms a pivotal connection 32 with one end of a connecting link 33, the other end of said connecting link forming a pivotal connection 34 with a clevis 35 of the caged spring device 2 for a purpose to be hereinafter disclosed.
  • a piston rod 36 is concentrically secured at one end to the side of piston 7 opposite valve stem 11 and extends axially out of casing 4 with its opposite end forming a pivotal connection 37 with connecting link 33.
  • the caged spring or force balancing device 2 in addition to the spring cage 30, also comprises a coaxially disposed screw-threaded operating rod 38 having the clevis 35 secured to an outer end thereof.
  • Operating rod 38 carries a tubular member having a screwthreaded nut 40 fixed on the end thereof adjacent clevis 35 for coaxially centering said rod within said tubular member and adjusting the axial positions relative to each other.
  • the other end of operating rod 38 is co axially centered in tubular member 39 by a centering nut 41 secured onto the corresponding adjacent end of said tubular member.
  • a spring retainer 42 is coaxially slidably supported on the rod 38 and tube 39 assembly adjacent an open end of spring cage 30 opposite the end fixed to connecting bar 27, and is provided with a plurality of ball bearings 43 to keep friction to a minimum during relative axial movement between the spring retainer and the rod and tube assembly;
  • a spring 44 has one end anchored to spring retainer 42 and the other end anchored to a spring retainer 45 axially spaced apart from said spring retainer 42 and coaxially disposed inwardly of spring cage 30 toward the closed end fixed to connecting bar 27.
  • the annular open end of spring cage 30 is normally in abutting, but separable, relation with the adjacent one of a pair of jam nuts 46 and 47 circumferentially carried by spring retainer 42.
  • Spring retainer 45 has formed thereon an annular flange 48 for normally making abutting contact with a snap ring 49 fixed internally of and between the ends of spring cage 30. Abutting contact of flange 48 with snap ring 49 is made with the side of said snap ring opposite spring 44, so that said retainer, in a manner to be hereinafter disclosed, may be moved axially out of contact with said snap ring in a direction toward the closed end of spring cage 30.
  • a tapered guide member 50 is coaxially fixed on the inner end of operating rod 38 and is adapted for engaging and disengaging a complementarily contoured recess 51 formed concentrically in the adjacent side of spring retainer 45.
  • operating rod 38 and jam nuts 46 and 47 are positionally adjusted relative to tubular member 39 and spring retainer 42, respectively, such that, when the several components of the servo positioner, that is, spool valve 10 and piston 7 of the control valve device 1, and piston 22 of the power cylinder device 3 are all in their respective neutral positions, in which they are shown in Fl(]. 1 of the drawings, guide member 50 should be resting in recess 51 without exerting any pressure against spring retainer 45, flange 48 of spring retainer 45 should be resting against snap ring 45 without exerting any pressure thereon, and the axial distance between spring retainers 42 and 45 should be such that spring 6 is subjected neither to compression or tension, but is in a totally relaxed state.
  • spool valve was moved leftwardly out of its neutral position to an initial supply position in which supply port 16 is communicated with delivery port 17, while delivery port 18 is communicated with exhaust port 20.
  • the right side of piston 22 of power cylinder device 3 is thus vented to atmosphere via conduit 23, delivery port 18 and exhaust port 20, while the left side of said piston is pressurized by fluid pressure supplied via delivery port 17 and conduit 21.
  • piston rod 25 With pressurization of the left side of piston 22, said piston and, therefore, piston rod 25 are moved to the right to an extended or operating position for effecting the desired operation or movement of the device or machine part (neither of which is shown) connected to stud 26, the amount of movement of said piston and piston rod being commensurate with the degree of the fluid pressure control impulse initiated by the operator and the resulting degree of fluid pressure supplied to the left side of said piston.
  • Rightward movement of piston rod 25 causes similar movement of connecting bar 27 and spring cage 30 which, acting through snap ring 49, moves spring retainer 45 to the right also, thus placing spring 44 under further tension.
  • actuator piston 7 When it is desired to position piston rod 25 out of its neutral position to a position to the left of neutral, the operator pressurizes the left side of actuator piston 7 which causes rightward movement of spool valve 10 and consequent venting of the left side of power piston 22 via vent port 19 while causing buildup of pressure acting on the right side of said power piston via delivery port 18 now communicating with supply port 16.
  • piston rod 36 When actuator piston 7 moves to the right, piston rod 36 also moves to the right which effects counterclockwise movement of connecting link 33 and consequent rightward movement of operating rod 38.
  • jam nut 47 by abutting against spring cage 30, prevents rightward movement of spring retainer 42, but guide member 50 acting against spring retainer 45, which is free to move to the right away from snap ring 48, causes rightward movement of spring retainer 45 and thereby places spring 44 under'tension.
  • Variations of control pressure acting on the left side of actuator piston 7 are effective for causing corresponding changes in the position of power piston 22 and piston rod 25 in a manner similar to that discussed above in connection with pressurization of the right side of actuator piston 7.
  • the servo positioner shown in FIG. 2 is arranged such that the neutral or zero position of the power piston 22 of power cylinder device 3 is at one end of the travel stroke, in this instance at the left end, as viewed in the drawing.
  • the servo positioner shown in FIG. 2 also comprises a caged spring or force balancing device 52 somewhat different from the caged spring device 2 of FIG. 1.
  • control valve device 1 and power cylinder device 3 are identical in structure to those shown in FIG. 1, identical reference numerals to those in FIG. 1 have been assigned to the corresponding components of said control valve device and power cylinder device shown in FIG. 2.
  • Spring device 52 which is operatively interposed between control valve device 1 and power cylinder device 3 in substantially axially parallel relation thereto, comprises a spring retainer 53 having a clevis 54 formed thereon, said clevis beingpivotally connected to the end of connecting link 33 opposite pivotal connection 32.
  • a screw-threaded support rod 55 has one end adjustably secured to connecting bar 27 and extends perpendicularly away therefrom toward and in axial alignment with clevis 54.
  • the opposite end of support rod 55 has a spring retainer 56 coaxially secured thereto in oppositely facing relation to spring retainer 53.
  • Spring retainers 53 and 56 are axially spaced apart with opposite ends of a spring 57 anchored thereto, respectively.
  • support rod 55 is positionally adjusted at connecting bar 27 so that the length of said support rod between said connecting bar and spring retainer 56 is such to maintain spring 57 free of either compression or tension, that is, in a relaxed state, when the several components of the servo positioner are in their respective neutral positions in which they are shown in FIG. 2 of the drawings.
  • control port 8 is not connected to control pressure but may be kept vented to atmosphere.
  • control valve device 1 functions in the manner above described in connection with the apparatus shown in FIG. 1 for effecting supply of operating fluid pressure to the left side of power piston 22 to cause said piston, piston rod 25, and stud 26 to be moved to the right to an operating position in which the machine part or device connected thereto is operated to a desired position.
  • FIG. 1 In similar manner as the apparatus shown in FIG.
  • control pressure acting on the right side of actuator piston 7 causes clockwise movement of connecting link 33, which, acting through clevis 54 and spring retainer 53, exerts a corresponding leftwardly directed tensional force on spring 57.
  • rightward movement of piston rod 25 and, therefore, of connecting bar 27 and support rod 55 exerts a rightwardly directed tensional force on spring 57 which brings about a balancing of the forces and consequent restoration of actuator piston 7 and spool valve to their neutral positions, with piston rod and stud 26 remaining in their established operating positions.
  • power piston 22 assumes either a new position or the neutral position.
  • the pressurized operating fluid supplied to the power cylinder device 3 for operation thereof may be either pneumatic of hydraulic.
  • Servo positioner apparatus for selectively positioning a mechanical member in a desired position and maintaining the mechanical member in said desired position until a change is effected, said servo positioner apparatus comprising:
  • a. power piston means connectable to the mechanical member and normally occupying a neutral position, said power piston means being movable out of said neutral position to a different position in response to operating fluid pressure;
  • control valve means comprising:
  • valve member having a cut-off position in which a supply communication via which operating fluid pressure may be supplied to said power piston means is closed and being operable to a supply position in which said supply communication is open, and
  • an actuator rod axially aligned with and having one end connected to said actuator member and the other end pivotally connected to said connecting link between the ends thereof for effecting rotational movement of the connecting link about its fulcrumed end and consequent axial movement of said operating rod in one direction, said axial movement of said operating rod being effective for subjecting said spring to a first tensional force acting in said one direction according to movement of said actuator member,
  • a connecting bar rigidly connecting one end of the power piston means to the other end of said connecting means for effecting axial movement thereof concurrently with and to a corresponding amount as that of said power piston means in a direction opposite to the axial movement of said operating rod for subjecting said spring to a second tensional force acting in a direction opposite to that of said first tensional force
  • said spring being cooperative with said operating rod, said connecting link, and said actuator rod member, upon attainment of a balanced state between the oppositely directed tensional forces for effecting restoration of said valve member to its said cut-off position.
  • said two-way means comprises:
  • said operating rod when moving axially in a first direction, being engageable with said first spring retainer and disengageable from said second spring retainer for effecting concurrent and corresponding axial movement of said first spring retainer only, and being engageable with said second spring retainer and disengageable from said first spring retainer, when moving axially in a second direction opposite to said first direction, for effecting concurrent and corresponding axial movement of said second spring retainer only, and
  • said connecting means being engageable with said second spring retainer and disengageable from said first spring retainer, when moving axially in a first direction oppositely to and concurrently with axial movement of said operating rod in its said first direction, for effecting concurrent axial movement of said second spring retainer in a direction corresponding to that of the connecting means, and being engageable with said first spring retainer and disengageable from said second spring retainer, when moving axially in a second direction oppositely to and concurrently with axial movement of said operating rod in its second direction, for effecting concurrent axial movement of said first spring retainer in a direction corresponding to that of the connecting means.
  • Servo positioner apparatus as set forth in claim 3, wherein said first spring retainer is provided with a coaxial bore through which said operating rod extends for abuttingly engaging said second spring retainer during movement of said operating rod in its said second di-' rection, said coaxial bore having ball bearing means disposed therein for providing friction free relative axial movement between the operating rod and the first spring retainer.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Servomotors (AREA)
US00289754A 1972-09-15 1972-09-15 Fluid pressure operable servo positioner Expired - Lifetime US3831490A (en)

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US00289754A US3831490A (en) 1972-09-15 1972-09-15 Fluid pressure operable servo positioner
JP48097384A JPS4992494A (2) 1972-09-15 1973-08-31
JP1977004787U JPS5325120Y2 (2) 1972-09-15 1977-01-20

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US00289754A US3831490A (en) 1972-09-15 1972-09-15 Fluid pressure operable servo positioner

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Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20050163639A1 (en) * 2004-01-28 2005-07-28 Government Of The United States Of America, As Rep. By The Admin. Of The Us Envirn. Pro. Agen. Hydraulic actuator control valve

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2126533A (en) * 1935-04-10 1938-08-09 Gen Electric Hydraulic governing mechanism
US2264262A (en) * 1940-04-09 1941-11-25 Charles Tagliabue Mfg Co Valve positioner
US2832200A (en) * 1954-12-10 1958-04-29 Kent Ltd G Control apparatus
US3290996A (en) * 1963-11-13 1966-12-13 Audco Ltd Remote control of fluid valves
US3316815A (en) * 1961-12-04 1967-05-02 Garrett Corp Servo-actuating mechanism for pneumatic analog computers
US3362296A (en) * 1965-08-20 1968-01-09 Bell Aerospace Corp Mechanical feedback stroke divider
US3693501A (en) * 1969-08-28 1972-09-26 Worcester Valve Co Ltd The Servo-systems

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2126533A (en) * 1935-04-10 1938-08-09 Gen Electric Hydraulic governing mechanism
US2264262A (en) * 1940-04-09 1941-11-25 Charles Tagliabue Mfg Co Valve positioner
US2832200A (en) * 1954-12-10 1958-04-29 Kent Ltd G Control apparatus
US3316815A (en) * 1961-12-04 1967-05-02 Garrett Corp Servo-actuating mechanism for pneumatic analog computers
US3290996A (en) * 1963-11-13 1966-12-13 Audco Ltd Remote control of fluid valves
US3362296A (en) * 1965-08-20 1968-01-09 Bell Aerospace Corp Mechanical feedback stroke divider
US3693501A (en) * 1969-08-28 1972-09-26 Worcester Valve Co Ltd The Servo-systems

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20050163639A1 (en) * 2004-01-28 2005-07-28 Government Of The United States Of America, As Rep. By The Admin. Of The Us Envirn. Pro. Agen. Hydraulic actuator control valve
WO2005073565A1 (en) * 2004-01-28 2005-08-11 Government Of The United States Of America, As Represented By The Administrator Of The Environmental Protection Agency Hydraulic actuator control valve
US7305914B2 (en) 2004-01-28 2007-12-11 The United States Of America, As Represented By The Administrator Of The Environmental Protection Agency Hydraulic actuator control valve

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Publication number Publication date
JPS5294594U (2) 1977-07-15
JPS4992494A (2) 1974-09-03
JPS5325120Y2 (2) 1978-06-27

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